Positive displacement pump for metering



Aug. 17, 1943. D SAMIRAN 2,326,803

POSITIVE DISPLACEMENT PUMP FOR METERING Filed March 18, 1941 2 Sheets-Sheet l 65s Tan/K Aug. 17, 1943. D. sAMlRAN 2,326,803

POSITIVE DISPLACEMENT UMP FOR METEING Filed March 18, 1941 2 Sheets-Sheet 2 /N VEN rol? to 'the engine.

Patented Aug. 17, 194.3

aszasos POSITIVE DTSPLACEMENT PUMP Fon.

METERING David Samiran,

Application March 18,

Dayton, Ohio 1941, Serial No. 383,977

`1 Claim. (Cl. 103-136) (Granted under the act amended April 30, 19

The invention described herein may be manufactured and used by or for the Government for governmental purposes, without the payment to me of any royalty thereon. n

This invention relates to yan improved rotary pump in which leakage losses are reduced to such Yan extent that the pump may be employed for pumping fuel from a source of fuel supply to a.

delivery conduit and measuring the quantity of fuel being pumped by counting the number of revolutions made by the pump and determining the rate of fuel delivery by determining the velocity of the pump rotor by means of a tachometer.

In aircraft fuel system it is of great importance to be able to determine the quantity of fuel consumed by the power plant and also to determine the rate of fuel consumption to check on whether the fuel mixture is proper for the existing operating conditions. In the fuel systems heretofore employed it has been necessary to insert both a quantity meter and a ow meter in the fuel delivery line to measure the quantity of fuel consu'med as well as the rate of consumption, since the fuel pump included a by-pass controlled by a pressure relief valve and hence its displacement had no relation to the quantity of fuel delivered The insertion of meters of the above type in the delivery line caused an increased pressure drop amounting to as much as two pounds per square inch and added as much as ten pounds to the weight of the fuel system components, apart from any remote indicating equipment. Further the adding of resistance in the fuel lines greatly accentuated the diculties encountered with vapor locking in the fuel systems of air-craft intended to operate at high altitudes. With the development of automati- I vision of a sealing means cally controlled remote drive fuel pump' systems such as illustrated in my United StatesPatent 2,229,132, in which the speed of the fuel .pump is automatically controlled to maintain a constant pressure in the fuel delivery line irrespective'of fuel demand, the necessity for the use of the ccnventional relief valve with the attendant vapor locking troubles was eliminated and it became apparent that if a pump could be developed having a suciently high volumetric elciency, A the pump could be directly employed asa fuel quantity meter so that separate meters would not be required. Reciprocating piston pumps cannot be employed in an automatically controlled fuel system of the character above described due to uctuating delivery pressure unless of the type having a large number of cylinders', and such of March 3. 1883, as

vided with mechanically actuated valve mechanism, thus making the pump very expensive to construct. The gear type pump has such a poor lvolumetric emciency that it cannot be employed as a meter, so that a movable vane type pump has been developed in which special attention has been devoted to sealing features which reduce the leakage losses to such an extent, that it now becomes possible to employ the pump for the dualfunction of a fuel pump and a meter, counting the number of revolutions of the pump to determine fuel delivered by the pump and employing a tachometerfor measuring speed 0f the pump' in terms of the, rate of delivery.

The principal object of the invention is the provision in a movable vane rotary pump for pumping and metering fluids of a pumprotor having radially movable vanes mounted in the sump casing of novel sealing means for preventing lleakage of liquid from the discharge to the inlet side of the pump along the radial contact faces of the pump vanes.

A further object of the invention is the profor the radial contact face of a movable pump vane, inA which the sealing means is made of resilient material in the form of a rectangulary body portion adapted to be inserted into a `corresponding groove on the radial face of the vane, the body portion being provided with laterally extending flanges which overlie at least a portion of the radial face of the vane, the said flanges being ared outwardly to form a cup shaped contact surface on their outer faces and leaving a clearance space on their rear faces adapted to be subjected to uid pressure from the iiuid within the pump to maintain a sealing pressureon the contact face of at least one of the flanges.

".,line 3 3 of Fig. 2.

a pump cannot -be used as a meter unless pro- Fig. 2 is a partial longitudinal a pump in accordance with the invention.

Fig. 3 is a transverse sectional view taken on v Fig. 4 is a top plan view pump illustrated in Figi 2. l

"`Fig. 5 is a perspective view illustrating a novel seal for the vanes of the pump of Fig. 2; and

sectional view of partlyin section of the with its attendant disadvantages.

Fig. 6 is a perspective view illustrating the action of the sealing means illustrated` in Fig. 5.

Referring to Fig. 1 which illustrates a portion of an automatic fuel system employing a pump in accordance with the present invention, the reference numeral I indicates a fuel supply tank connected by means of a conduit 2 to a fuel collector 3 which may incorporate fuel shut-off cocks (not shown). Fuel from the collector 3 is drawn into the inlet side of the fuel pump, lgenerally indicated by the reference numeral I0, through a conduit 4 and fuel is discharged by the pump into a delivery conduit 5 which is connected to the float chamber of an aircraft engine carburetor 6 which supplies fuel for consumption by the associated aircraft engine. The pump I0, which forms the subject matter of the present invention, is adapted to be driven by means of a hydraulic motor 'I0 which has its inlet side connected by means of a conduit 'II and its outlet side connected by means of a conduit 12 respectively to the outlet and inlet sides of a suitable engine driven pressure gensure in the conduit 5 having been attained. The indicator 80 is graduated, instead of in terms of speed, to indicate the fuel consumption in terms of gallons per hour or other convenient unit in- 5 dicative of the rate of fuel consumption by the erator or pump (not shown). The quantity of fluid admitted to the motor and hence its speed being controlled by means of an automatic pressure responsive control device subjected to the variation in pressure in the pump delivery line 5 adjacent the point of delivery to the carburetor float; chamber 6. Such-pressure generator and control device are not illustrated, being fully described in my crore-mentioned United States Patent No. 2,229,132. The function of the automatic control is to maintain the speed of the hydraulic motor, and hence thespeed and output of the fuel pumpl I0, such that the fuel pressure in the delivery conduit 5 at the point of delivery to the engine carburetor remains substantially constant irrespective of the demand for fuel by the engine, eliminating the customary relief valve The fuel pump I0 is so constructed, as hereinafter more fully described, that it constitutes a positive displacement pump having a very high volumetric efficiency over its entire range of speed so that by counting the number of revolutions of the pump the quantity of fuel delivered by the pump from the fuel supply to the engine carburetor for consumption by the engine may be readily deter'. mined in terms ofgallons of fuel consumed or other convenient measuring units. It is also possible to determine the rate of fuel consumption by the engine by simply measuring the velocity of the pump by means of a suitable tachometer which indicates the pump speed in terms of the rate of fuel consumption such as gallons per hour. In order to measure the pump speed 'and hence the rate of fuel consumption a tachometer-gen- 'erator 15 of well-known construction is secured to an extension driving shaft of the hydraulic motor 'l0 so that the armature of the tachometer- 'w generator rotates in unison with the motor driving shaft and the rotor of the fuel pump. The

ltachometer-generator '|5.is electrically connected in series with one switch element of a two circuit pressure responsive switch 18 and with an indicator 80 which is constructed as a volt meter and together with the tachometer-generator 15 forms an electric tachometer or speed measuring device well-known in the art. The pressure responsive switch 18 of a well-known construction, is connected by means of a branch conduit 5' to the delivery conduit 5 adjacent the carburetor 6 and isoperative to close the electrical circuit between the tachometer-generator 15' and the indicator/BO only upon a predetermined fuel presassociated engine. The indicator 83 will give a close approximation of the instant rate of fuel consumption because of the fact that the fuel pump I0 is so designed that one revolution thereof displaces a definite volume of fuel so that the number of revolutions per unit of time determines the rate of delivery of fuel to the engine carburetor 6, and hence the rate of fuel consumption by the engine. In order to measure the quantity of fuel displaced by the pump I0 a cam- /actuated switch device 85 is incorporated with the tachometer-generator 'I5 to be driven thereby at a reduced speed, -the cam-actuated switch being so designed that it closes an electrical circuit once in a predetermined number of revolutions of the pump IU, for example the number Y of revolutions of the pump corresponding to the delivery of one gallon of fuel.` The cam-actuated switch 85 is electrically connected in series with a secondswitch device incorporated in the pressure responsive switching device 13 and also connected to a conventional solenoid actuated counting device 90, the circuit including a battery or other source of direct current (not shown). The counting mechanism is operative to indicate each gallon of fuel delivered by the pump I0 to the conduit 5 and by means -cf a suitable dial mechanism indicates the total number of gallons delivered by the pump since it; was started. The counter mechanism 90 may be of any wellknown construction and incorporates a suitable resetting mechanism (not shown). The pressure responsive switch device 18 is also operable to close the circuit between the cam-actuated switch 85 and the electrical counter mechanism 90 only upon the fuel pressure in conduit 5 at the point of delivery exceeding a minimum pressure, so that both the counter mechanism and the tachometer electric circuits are inoperative when thefuel pump is not delivering fuel to the engine carburetor.

` The above described fuel system, apart from the pump I0, forms no part of the present invention, but illustrates the manner in which the novel fuel pump is utilized to serve the dual function of a pump and a meter, and the specific construction of the fuel pump Ii), whereby its volumetric efciency may be maintained sufficiently high in order to accomplish its metering function, will now be`described.

Referring now to Figs. 2 and 3, the rotary pump generally indicated by the reference numeral I0 is seen to comprise a generally cylindrical pump body or casing II provided with the central substantially cylindrical cavity I-2, forming a pump chamber and, -as seen in Fig. 3, the chamber I2 (communicates with the diametrically disposed ports I3 and I4, which extend into respective threaded bosses I5 and I6, and the ports I3 and I4 alternately serving as inlet and discharge ports depending upon the direction of rotation of the pump rotor. The ports I3 and I4 are each enlarged at the point of communication with the chamber I2 by means of the arcuate recess I1 0 cut into the chamber wall. The pump bodylil is provided with a longitudinally extending bore l'into which is pressed a suitable bronze bushing p I9 which servesas a journal for the pump vrotor driving shaft 20. The pump casing I I is provided 5 with an annular-sleeve-like extension v2| which sei-ves to 4house the outer end of the rotor shaft A 20 and also serves to house a shaft sealing means comprising a cupgshap'edsealing gasket 22Itmade of synthetic rubber, which is held by .a retaining ring 23made of livrornfeA or suitable antifiction inlet and dischargeports. For service as a fuel pump of the character described, where themaximum `fuel pressures seldom exceed six pounds material, into-abutting engagement with th'elend,. .f

of thebearing sleeve I9 and also in sealing.. en-,I

gagement' with the periphery of the shaft'20 tov prevent leakage of fluid axially along the shaft.H spring,

The retaining "ring 23 is engaged by a abutment washer 24, which is urged into engage# ment vwith the retainer ring 23 by means of the spring -25 concentrical'ly arranged.- on" the shaft 20 and having its outer, end resting against an' abutment washer 26 which is restrained against axial movement along the shaft by means fof a`.-

taper-pin 2'I. Thespacing between the spring abutment washers 24 and 26 is so arrangedl'thatv the initial compression loading of the spring a suitable universal coupling 30 which maybe connected to the hydraulic motor l0, Fig. fzlfto drive the rotor shaft 2li. The axis of rotation of the rotor shaft 20 is arranged to be eccentric i with respect to thelongitudinal axis of the pump chamber I2 and the shaft is' provided at its `inner end with a rotor 32'integrally formed therewith;

The rotor 32 .is arranged in the form of a cylin:

drical annulus having a'centrally disposed cyl'nf- `drical cavity 33 andis/"suitably longitudinally' slotted as atl 34 to accommodate the radial Inov:l able vanes 35 (see Fig.- 3), the outer portions o the vanes 35 contacting the walls ofthe pump chamber I2 and on their inner ends bein'g'fin contact with an axiallyk disposed floatingcoilj i spring 36 which is wound on a threaded ore member 38 and located infthe rotor cavity' 33.

The depth of the threads 1-3`I (Fig. 2) of the Acorejy member 38 being cut-sufficiently deep that'the coil springl 36 when movedradially inwardv may come substantially flush with the outer periph-j' ery of the core member. -The coil spring 36 Vis;l

made slightlyless in length than the core member 38 so that as the spring is compressed ra-" dially inward'it may increase its axial lengt-h(V`` The spring and core member V38 freely float-'fin the cavity or chamber 33jfo'rmed in' the pump 35 into contact with the wallsf the pump charnber I2. The provision of the coil type of spring allows the shape of portions of the pump cham-,

charge and the pump inlet ports, for example from port I3 to port I4, a sealing member 4Q is provided extending longitudinally of the pump rotor 32 and movable in a slot 4I formed in the upper part of the pump casing and pressed downrotor 32 and the coil spring serving as a means for constantly yieldingly urging the pump vanes);

per sguare inch, 'this seal has beenfound very effective andv substantially eliminates all leakage between the pumpdisch'arge and the pump inlet tangentially along the line of contact of the sealing element with the rotor 32.

The outer end of the pump casing I Ian'd pump chamber I2 is open, and the open end of the pump chamber is'v adapted to be closed-by means of a circularsealing ring which abuts in sealing engagement with the outer end face of the rotor 32 and the radial lend faces of the pump vanes 35, the latter being arranged to come flush with the outer end face of the pump rotor. The sealing ring 45 may be made of any suitable material or composition such as Duralumin, cast iron or Bakelite and is secured against rotation relative to the pump casing by means of a pair of circular keys 46 which extend partially into the pump housing and into .sealing disc 45, allowing the sealing disc however to move axially into' `phra'gm 4'I`.befng maintained into tight sealing engagement with the rear face' of the sealing disc 45 by means of a' bearing disc 48 and al leaf spring 49 which yieldingly engages an annular end cover 50 secured to the casing II by means of suitable screws 5I. The leaf spring 49 causes an axial pressure on the disc 48 which transfers this pressure through the exible diaphragm 41 to the Sealing disc 45 retaining 4the latter in tight sealing engagement with the end face of the rotor 32 and the radial faces of the pump vanes 35. The axial thrust of the spring 49`also maintains the innerend face ofthe rotor 32 in tight sealing engagement with the inner end w-all of the pump chamber I2 and the inner radial end faces Of the vanes 35 are held insealing engagement with the end walls of the rotor slots 34, the slotsbeing carefully ground so' that the vanes 35 may reciprocate therein, butI having a suciently sm-all clearance so that anyleakage radially inward Iing an adequate seal against leakage radially in-- ward along the outer end face and the rotor 32 and the outer radial faces of the pump vanes 35.

The flexible diaphragm 41 insures that there will be no leakage of the fluid from the pressure side gg the pump axially'into the :annular end cover wardly into sealing engagement with the periphery of the pump' rotor by means of a thin leaf spring 42. The sealing element 49 is-preferably made of a semi-hard synthetic rubber compound which is unaffected by gasoline or similar fuels and, being/freely oating, can accommodate itself to slight irregularities on the rotor surface, but

Y st ill maintain an adequate seal between the pump When the pump is in operation, and rotating for example fin a clockwise direction as seen in Fig. 3, the pump will pick upV fluid in the clearance space between the'rotor and the walls of the pump chamber I2 between adjacent pairs of vanes and will transfer this fluid to the outlet side of the pump-through the outlet port I3 developing pressure therein. Any .adjacent pair of vanes `form together with Athe clearance space therebetween at the peripheryof the rotor an expansi-ble chamber which expands as it comes into register with the pump inlet port,- remains of substantially constant volume until it begins to register with the outlet port, and then decreasing in Avolume to zero as the vanes move away from the outlet port toward the inlet port. When the pump is delivering fuel under pressure a portion of the'inner surface of the sealing the necessity for using a very heavy spring toobtain the necessary sealing pressure on the sealing disc 45, fluid pressure is admitted to chamber 52 formed behind the flexible diaphragm 41 by means of the annular cover 50, this uid under pressure being admitted to` the chamber 52 as seen in Fig. 4 by means of one of two drilled ports 54 formed inthe pump body il yand each respec-v .tively communicating with one of the ports i3 and I4.' The flexible diaphragm 41 is provided with a suitable aperture 55 adapted to register with one of the passages I4 to allow the passage of fluid under pressure therethrough -to a blind.I

passage 56 formed in the cover plate 5I). `A small drilled passage 5l in the cover plate connects the sembled in the pump of Fig. 2 the contact face ofthe flanged portion of the seal Il will extend well belowV the outer periphery of the rotor I2 and will form a cup shaped seal and as seen in Fig. 6 fluid under pressure from the discharge side of the pump can enter behind the forwardly moving flange portion l2 and force the flange into tight sealing engagement with the sealing disc 45, and as the vane moves out of register with the discharge port the flange 62 on the oppositeside of the vane will be subject to the dissealing pressure on at least one of the sealingr flanges 62. The rectangular shank or body porchamber 52 with the passage 56 so that the iiuid under pressure from the discharge port acts on the diaphragm 41 to assist the spring 49 in maintaining a proper load-on thesealing disc 45 and relieving the outward thrust on the sealingdisc.

The cover plate 50 and flexible diaphragm 41 may beirotated on assembly to havethe aperture 55 and passage 5B to register with the proper one of the passages 54 which will communicate with the pressure side of the pump, depending on the direction of rotation of the` pump. When the pump is being started the chamber 52 will be subjected to atmospheric pressure while the interior 'of the pump casing will be under suction so that the pressure within the chamber 52 will' maintain an adequate sealing force when the pump is being primed.

- Fig. 5 illustrates an improved` form of seal for the end faces of the pump vanes of the pump of Fig. 2 and may be employed at one or both ends of a respective Vane. To accommodate the seal the radial endface of the vane is slotted longitudinally as at a and is cut back or recessed as indicated at 35h. The resilient seal made of synthetic rubber and indicated generally by the reference numeral S0 is lformed with a rectangular shank portion BI which is adapted to be forced into the vane slot 35a and at its upper end the seal is provided with outwardly flared flange portions 62 which merge into therbody portion and overlie the end faces of the recessed portion 35h of the vane 35 with a. slight clearance on the rear face of the flanges. When astion 'Si of the seal 60 serves to prevent leakage along the slot :Sato the lower end of the pump vane'and also serves -to maintain a good sealing contactalong its outer face`with the sealing disc 45. When seals 'of the type shown in Fig. 6 are used at both ends ofthe vaneit will of course be necessary to havel the rotor'slots 34 extend the full length of the rotor 32.

Although the novel features of the present invention are illustrated as being applied to a fluid pump it is to be understood that these features may also apply to fluid pressure actuated motors of the movable vane type and the term pump as employed in the claims is intended to also embrace uid actuated motors structional character.

Although only preferred forms of the invention have been illustrated many changes therein will become apparent to those skilled in the art as falling within the scope of. the invention as defined by the appended claim.

I claim:

In an expansible chamber device of the character having a vaned rotor -therein lwith the vanes thereof radially movable therein, of means for sealing the radial edges of the vanes comprisng, a slot extending along the radial face of each vane, a recessed portion adjacent the outer radial partl of the vane, a resilient sealing member having a shank portion adapted to be inserted in the slot in said vane, said sealing member having outwardly flared and laterally extending flange portions adapted to overlie the recessed portion of the vane, the contact face of the flanges being cup-shaped and-the rear face of the flanges having a clearance from the edges of the recessed portion of the'vane to allow the' action of fluid pressure thereon.

DAVID SAlillIRAN.

of the same con-v S 

